WO2011076169A2 - Dispositif de pendule centrifuge - Google Patents

Dispositif de pendule centrifuge Download PDF

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Publication number
WO2011076169A2
WO2011076169A2 PCT/DE2010/001453 DE2010001453W WO2011076169A2 WO 2011076169 A2 WO2011076169 A2 WO 2011076169A2 DE 2010001453 W DE2010001453 W DE 2010001453W WO 2011076169 A2 WO2011076169 A2 WO 2011076169A2
Authority
WO
WIPO (PCT)
Prior art keywords
pendulum mass
pendulum
mass carrier
carrier
gap
Prior art date
Application number
PCT/DE2010/001453
Other languages
German (de)
English (en)
Other versions
WO2011076169A3 (fr
Inventor
Stephan Maienschein
Christian HÜGEL
Stefan Jung
David SCHNÄDELBACH
Original Assignee
Schaeffler Technologies Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to EP10805584.9A priority Critical patent/EP2516887B1/fr
Priority to CN201080059074.2A priority patent/CN102762887B/zh
Priority to JP2012545084A priority patent/JP5746209B2/ja
Publication of WO2011076169A2 publication Critical patent/WO2011076169A2/fr
Publication of WO2011076169A3 publication Critical patent/WO2011076169A3/fr
Priority to US13/528,170 priority patent/US20120255394A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2121—Flywheel, motion smoothing-type
    • Y10T74/2128—Damping using swinging masses, e.g., pendulum type, etc.

Definitions

  • the invention relates to a centrifugal pendulum device, comprising at least one pendulum mass carrier and at least one pendulum mass disposed thereon, which is at least a rolling element within recesses in the pendulum mass carrier and the pendulum mass formed raceways relative to the pendulum mass carrier radially and limited in the circumferential direction, wherein the rolling element a Having in the gap between the individual pendulum mass and pendulum mass carrier trained guide means.
  • speed-adaptive absorbers are used for the eradication of vibrations over a wide, preferably the entire speed range of the driving machine. These are able to eliminate torsional vibrations over a larger speed range, ideally over the entire speed range of the prime mover, by running them and arranged so that their natural frequency is proportional to the speed.
  • Such absorbers work on the principle of a centrifugal pendulum in the centrifugal force field. These comprise a pendulum mass carrier rotatable about an axis of rotation and oscillating on this inertial mass or pendulum masses mounted about the axis of rotation of the pendulum mass carrier. The individual pendulum masses are anxious to initiate a rotational movement to orbit the axis of rotation as far as possible.
  • pendulum masses move relative to the torque introduction axis either purely translationally on a circular trajectory or the trajectory has a radius of curvature changes at least in sections with increasing deflection of the pendulum mass from the middle position.
  • a generic centrifugal pendulum device in a drive train of a motor vehicle with a rotatable pendulum mass carrier and in pairs oppositely arranged pendulum masses is known.
  • the pendulum masses are limited movable by means of rolling elements relative to the pendulum mass carrier, for which purpose the rolling elements are limited in movable paths formed by recesses in the pendulum mass carrier and in the pendulum masses.
  • the recesses are formed as continuous slots with kidney-shaped curvature.
  • the resulting relatively large gap distance between the pendulum mass carrier facing surface of a single pendulum mass and the pendulum mass carrier allows tilting of the pendulum mass against the pendulum mass carrier, which can be a significant problem especially at low speeds and thus low centrifugal force.
  • the operation of the centrifugal pendulum in this speed range is then impaired and not sure reproducible for the recurrence case.
  • the tilting can also lead to damage to the individual components and the compounds and the pendulum bearing of the pendulum mass on the pendulum mass carrier.
  • the object of the invention is to provide an improved centrifugal pendulum device with reduction of the tilt tendency of the individual pendulum masses against the pendulum mass carrier and high stability.
  • a centrifugal pendulum device comprising at least one pendulum mass carrier and at least one pendulum mass disposed thereon by means of at least one rolling element within formed by recesses in the pendulum mass carrier and the pendulum mass raceways and by the pendulum mass and the pendulum mass carrier sweeping rolling element relative to the pendulum mass carrier radially and circumferentially is limited movable, wherein the rolling element has a formed in the gap between pendulum mass and pendulum mass carrier guide means, characterized in that in the gap between pendulum mass and pendulum mass outside the raceways for the rolling element and the rolling over the rolling element of the rolling element by the guide means swept area of the gap to- least locally limited reduction of the gap distance between pendulum mass and pendulum mass carrier are provided.
  • the gap between a single pendulum mass and the pendulum mass carrier is understood to mean the space between a pendulum mass and the pendulum mass carrier extending in the axial direction and formed in the radial direction and circumferential direction.
  • the position of the gap varies with the position of the individual pendulum mass in deflection due to the influence of centrifugal force.
  • the gap width which determines the axial distance between pendulum mass and pendulum mass carrier, is measured in each case between the mutually facing surfaces of pendulum mass and pendulum mass carrier.
  • the gap width can be constant over the entire extent of a single end face of a single pendulum mass directed toward the pendulum mass carrier or else vary in the direction of extent in the radial direction and / or in the circumferential direction.
  • the first basic embodiment is characterized in that at least one or more such means are provided which are each arranged and effective only in at least a portion of the gap between the pendulum mass and the pendulum mass carrier.
  • This embodiment offers the advantage that locally a gap reduction can be achieved in a targeted manner, wherein the number and / or geometry and / or dimensioning and / or arrangement of the means in the gap in dependence on the geometry and dimensioning of the centrifugal pendulum, in particular the individual pendulum mass.
  • the means are smaller than the individual pendulum mass in terms of their dimensions, it is possible to resort to standardized spacer elements, irrespective of their geometry, which can be integrated in a particularly advantageous manner into the spacer of the pendulum mass to the pendulum mass carrier.
  • an arrangement of the means for at least localized reduction of the gap distance between pendulum mass and pendulum mass carrier is selected in the first basic design, which is symmetrical relative to the pendulum mass.
  • the second basic design is characterized by a design of the means for at least localized reduction of the gap distance over the entire extent of the gap in the radial direction and in the circumferential direction outside of the raceways for the rolling element and the case of rolling the Abrollides swept by the guide means range between pendulum mass and pendulum mass carrier ,
  • This design has the advantage of setting a constant gap distance between pendulum mass and pendulum mass carrier.
  • the means for at least localized reduction of the gap distance of the pendulum mass are assigned, preferably coupled to the pendulum mass or formed on this.
  • the assignment to the pendulum mass advantageously provides a simple way to increase the mass of the pendulum.
  • the assignment to the pendulum mass allows the use of standardized pendulum mass carrier and avoids modifications to this.
  • the means for at least localized reduction of the gap distance associated with the pendulum mass carrier preferably coupled to the pendulum mass carrier or formed on this.
  • This embodiment allows a simple consideration of such required means for at least localized reduction of the gap distance in the production of the pendulum mass carrier, which are einarbeitbar depending on the type and design in one step in this.
  • the third possibility is characterized by the combination of both aforementioned possibilities, whereby in this embodiment the advantages of both variants can be partially combined with each other.
  • the individual means for at least localized reduction of the gap distance can be distinguished according to a first variant between the use of separate additional elements and according to a second variant of the integral training on at least one of the components - pendulum mass and / or pendulum mass carrier.
  • the embodiment according to the first variant has the advantage that the means for at least localized reduction of the gap distance can also be subsequently integrated into existing centrifugal pendulum devices or retrofitted.
  • additional elements in the form of standard elements can be used in a particularly advantageous manner, which can be connected easily and at least indirectly indirectly with little effort with the pendulum mass or pendulum mass carrier.
  • the means comprise at least one additional element in the form of a washer.
  • This can be a standard component.
  • additional elements can be arranged in a simple manner between pendulum mass and pendulum mass carrier without any necessary modifications.
  • the washers can be connected to the pendulum mass carrier or a single pendulum mass or loosely inserted with a suitable positional fixation, for example on already provided axial abutment surfaces on a standoff bolt and held by the connection of the pendulum mass with the axial end portion of the spacer bolt in the gap.
  • the means comprise at least one additional element forming at least one projection protruding into the gap.
  • the additional element can be embodied, for example, in the form of one of the following components:
  • a further sub-variant of this first variant is by the use of an over the entire surface of the individual pendulum mass on the pendulum mass carrier facing end face with the exception of the raceways and an area around this, which can be painted over by the individual guide means, extending additional element, in particular in the form of a Slice characterizes.
  • This design is characterized in the entire pendulum mass range in the undeflected state by a constant gap distance.
  • each two pendulum masses are arranged in pairs opposite each other on a pendulum mass carrier and coupled via spacers and determined in their position to each other, can in particular Advantageously, such an already anticipated spacer element or a spacer bolt for fixing the means for at least localized reduction of the gap spacing in functional concentration to be used.
  • the means are at least locally limited
  • localized projections formed in the axial direction for reducing the gap distance can be produced by appropriate shaping or machining of the surface of the pendulum mass and / or of the pendulum mass carrier.
  • at least one region on the pendulum mass and / or the pendulum mass carrier can be designed at least in sections.
  • the embossments form projections directed into the gap. This is an area at least partially impressed about the career of the pendulum mass and / or the pendulum mass carrier and the guide means is receivable in the recess formed by the embossing.
  • the pendulum mass can be arranged closer to the pendulum mass carrier and the space requirement of the centrifugal pendulum device is reduced.
  • the means for at least localized reduction of the gap distance of at least one enforcement of the pendulum mass and / or the pendulum mass carrier are formed.
  • Enforcements are formed due to the displacement of material under pressure and corresponding deformation.
  • the enforcements are to be arranged such that the thereby formed on the opposite end faces of pendulum mass and / or pendulum mass carrier due to the material displacement projections outside the raceways for the rolling element and outside of the paintable area for the guide means.
  • the formation of penetrations allows a targeted and simple arrangement of axial projections in the desired manner to reduce the distance.
  • the inventive design of a centrifugal pendulum device is used in a particularly advantageous manner with a torsional vibration damper in a drive train of a motor vehicle.
  • the torsional vibration damper comprises an input part and a relative to the input part against the action of energy storage elements limited rotatable output part and one or more damper stages.
  • the centrifugal pendulum device can be arranged on a disk part of the damper stage, for example on the input part, an optional intermediate part or the output part.
  • the inventive design of a centrifugal pendulum device is also used in a torque converter with a torsional vibration damper with a centrifugal pendulum device arranged thereon.
  • the torsional vibration damper may be arranged with the centrifugal pendulum device within a housing of the torque converter.
  • Another advantageous field of application is the use in a dual-mass flywheel, in a double clutch, in a wet clutch or in a dry clutch.
  • Figure 1 shows a section of an inventively designed
  • FIG. 2 a shows an embodiment of a centrifugal force-dispensing device according to the prior art in a sectional view A-A according to FIG. 1;
  • FIG. 2b shows an embodiment of a centrifugal-force-dispensing device according to the prior art in a sectional view B-B according to FIG. 1;
  • FIG. 2c shows an embodiment of a centrifugal force-dispensing device according to the prior art in a sectional view C-C according to FIG. 1;
  • FIG. 3 a shows a first embodiment of a design according to the invention
  • FIG. 3b shows a first embodiment of a design according to the invention
  • FIG. 3c shows a first embodiment of a design according to the invention
  • Figure 4a shows an embodiment of a first variant of a first
  • FIG. 4b shows an embodiment of a first variant of a first one
  • FIG. 4c shows an embodiment of a first variant of a first embodiment
  • Figure 5a shows a further development of a first variant of a first
  • FIG. 5b shows a further development of a first variant of a first embodiment
  • FIG. 5 c shows a further development of a first variant of a first one
  • FIG. 6 shows a second embodiment of a first variant of a first embodiment
  • FIG. 7 shows a third embodiment of a first variant of a first embodiment
  • FIG. 8a shows a first embodiment of a design according to the invention
  • FIG. 8b shows a first embodiment of a design according to the invention
  • FIG. 8c shows a first embodiment of a design according to the invention
  • FIG. 9a shows another embodiment of a second variant of a first one
  • Centrifugal pendulum device in a sectional view A-A according to Figure 1;
  • FIG. 9b shows a further embodiment of a second variant of a first one
  • FIG. 9 c shows a further embodiment of a second variant of a first one
  • Centrifugal pendulum device in a sectional view C-C of Figure 1;
  • FIG. 10 shows a particularly advantageous further embodiment of a second variant of a first basic embodiment of a centrifugal pendulum device according to the invention in a sectional view A-A according to FIG. 1.
  • FIG. 1 shows a simplified schematic representation of a detail of a view of from an inventively designed speed adaptive absorber in the form of a centrifugal pendulum device 1.
  • This preferably comprises a plurality of pendulum masses 2 acting inertial masses, which are mounted on a rotatable pendulum mass carrier 3 relative to this movable.
  • the storage is commuting.
  • the pendulum mass carrier 3 is preferably designed as an annular disc-shaped element.
  • the individual pendulum masses 2 are arranged at uniform intervals in the circumferential direction and viewed at the circumferential direction. In the illustrated section, only one pendulum mass 2A of a pendulum mass unit 2 is shown.
  • the representation of the axis of rotation R is only for clarity and not on the correct scale.
  • the inventive design of the mounting of the individual pendulum masses 2A, 2B on the pendulum mass carrier 3 is described in the sectional views AA, BB, CC for the individual variants of the two basic embodiments in Figures 3 to 10.
  • the sectional views AA, BB, CC in FIGS. 2a to 2c illustrate the problem of a tilting of the pendulum masses 2A ' , 2B ' with respect to the pendulum mass carrier 3 ' , which occurs in the case of an embodiment of a centrifugal pendulum device 1 ' according to the prior art.
  • the individual components are additionally marked with " ' " in this figure.
  • pendulum masses 2A, 2B are arranged in pairs opposite each other on both sides of the end faces 4.1 and 4.2 of the pendulum mass carrier 3.
  • the individual pendulum masses 2A, 2B essentially have a circular ring segment-like shape.
  • the mutually opposite at the end faces 4.1, 4.2 of the pendulum mass carrier 3 pendulum masses 2A, 2B are connected to form a single pendulum mass unit 2.
  • the compounds are denoted here by 11.1, 11.2, 11.3.
  • the connections 11.1 and 11.2 are respectively reproduced on the basis of sectional views AA and CC according to FIG. 1 in the following figures. The statements made for the connections 11.1, 11.2 also apply analogously to the connection 11.3.
  • connection takes place in the simplest case via a connecting element, which at the same time assumes the function of adjusting the distance between the paired pendulum masses 2A, 2B.
  • a spacer pin 12.1 for the connection 11.1 and a spacer pin 12.2 for the connection 11.2 use.
  • the standoffs 12.1, 12.2 are each passed through the pendulum mass carrier 3.
  • a solid connection of both pendulum masses 2A, 2B is realized to form the pendulum mass unit 2.
  • the single spacer pin 12.1, 12.2 is designed as a stepped bolt, each comprising two axial abutment surfaces
  • the spacer bolt 12.1, 12.2 is designed with its guided by the pendulum mass carrier 3 area 16.1, 16.2 such that it is greater than the width b of the pendulum mass carrier 3 and thus on both sides between the pendulum masses 2A, 2B and the pendulum mass carrier 3, a distance a is generated , This is measured, as already stated, from the width of the range 16.1 respectively
  • the attachment of the individual pendulum mass 2A, 2B on the standoffs 12.1, 12.2 is force and / or positive ,
  • This can be realized, for example, via axial securing elements, by means of which the individual pendulum masses 2A, 2B are respectively braced against the axial abutment surfaces 13.1, 14.1 or 13.2, 14.2, or, in a particularly advantageous embodiment, non-detachably form-fittingly by means of rivet connections 17.1, 18.1 or 17.2, 18.2 ,
  • the rivets in integral design on the spacer bolts 12.1, 12.2 are formed with and are formed during assembly.
  • the oscillating mounting of the individual pendulum masses 2A, 2B takes place via at least one pendulum bearing arrangement, here two pendulum bearing arrangements 5.1, 5.2, comprising rolling elements 8 designed as rolling bodies or rollers, which are mounted on a corresponding track. leads are.
  • the structure of a pendulum bearing assembly will be explained by way of example with reference to the pendulum bearing assembly 5.1. This is reproduced as a sectional view BB in the following figures. In this case, the movement of the individual pendulum mass 2A, 2B relative to the pendulum mass carrier 3 in the case shown by guided in raceways 6A, 6B and 7 and designed as rolling elements or rollers rolling elements 8 allows.
  • the raceways 6A, 6B are recessed for each pendulum mass 2A, 2B from this, the track 6A from the pendulum mass 2A and the track 6B from the pendulum mass 2B.
  • the raceway 7 is recessed from the pendulum mass carrier 3.
  • the recess takes place in the form of passage openings with the geometry adapted to the desired contour of the raceways 6A, 6B or 7.
  • embodiments of raceways 6A, 6B are conceivable by recesses incorporated into the pendulum mass 2A, 2B.
  • the geometry and dimensioning of the individual raceways 6A, 6B, 7 determines the allowable range of motion for the individual pendulum mass 2A, 2B.
  • guide means 19, 20 are provided on the individual rolling element 8, which are designed, for example, as a radial extension and, in the case shown, are designed in an integral design with the rolling element 8 to form shoulders.
  • paired opposing guide means 19, 20 of a rolling element 8 are arranged at a suitable axial distance from each other, which substantially corresponds to the width b of the pendulum mass carrier 3 in a region around the raceway 7.
  • the distance between the guide means 19, 20 to each other and the width of these guide means 19 and 20 determines the required minimum distance a m i n between the individual pendulum mass 2A and 2B and the pendulum mass carrier 3 in the area of Pendellageranordung 5.1, 5.2. This can not be reduced arbitrarily.
  • the greater this distance a m i n the more the individual pendulum masses 2A, 2B can be tilted sideways under certain operating conditions, which frequently occurs in particular at low centrifugal force or rotational speed.
  • Figures 2a to 2c illustrate the coupling of the individual pendulum masses 2A ' , 2B ' to the pendulum mass carrier 3 corresponding to the three sectional views AA, BB and CC of Figure 1 according to the prior art. Recognizable here is the minimum distance a min ' between pendulum mass 2A ' , 2B ' and pendulum mass carrier 3 ' over the entire extent of the pendulum mass 2A ' , 2B ' relative to the pendulum mass carrier 3 ' due to the axial width of the guide means 19 ' , 20 ' .
  • the first variant is characterized by the provision of separate additional elements.
  • the embodiments in the following figures correspond to sectional views A-A, B-B and C-C corresponding to FIG. 1.
  • FIG. 3a to 3c illustrate a first variant of a second basic embodiment in the above-mentioned sectional views AA, BB, CC according to FIG. 1.
  • FIG. 3a illustrates the sectional view AA according to FIG. 1.
  • the means 21 each comprise an additional element in the form of a disc-shaped element 22 , 23, wherein each of the additional elements between the pendulum mass carrier 3 and arranged on the respective end face 4.1 or 4.2 whose pendulum mass 2A, 2B is arranged.
  • the additional elements in the form of disc-shaped elements 22 and 23 are designed and arranged such that they are arranged in the radial direction and in the circumferential direction in each case over the entire extent of the mutually facing end faces 15A, 15B of the individual pendulum masses 2A, 2B Formation of the raceways 6A, 6B and 7, of the area swept by the guide means 19, 20 range in the gap and the passage openings for the connecting elements of the compounds 11.1, 11.2 and 11.2 are
  • FIG. 3a shows the view AA according to FIG. 1. This shows the entire area of the individual additional elements on the end faces 15A, 15B of the pendulum masses 2A, 2B, the arrangement between them and the axial stop surfaces 13.1, 13.2 of the spacer bolt 12.1, the passage openings 31 , 32 for the axial end portions of the spacer bolt 12.1 and the producible with this reduced distance A v between pendulum mass 2A, 2B and pendulum mass carrier 3.
  • the additional elements in the form of disc-shaped elements 22, 23 are associated with the pendulum masses 2A, 2B and attached thereto. The attachment takes place via the already existing spacer bolt 12.1, wherein the axial end portions are formed such that they are adapted to form a rivet head for forming a rivet 17.1, 18.1.
  • FIG. 3b shows a sectional representation B-B through the pendulum bearing arrangement 5.1.
  • Recognizable here is the required in the area of the guide means 19, 20 and of these swept during rolling of the rolling element 8 area required minimum distance a mjn between pendulum mass carrier 3 and individual pendulum mass 2A, 2B. It can also be seen that the individual disc-shaped element 22, 23 is recessed in each of these areas while providing the minimum distance a mi n for this area, ie openings or through openings 33, 34 which are preferably larger than the areas to be kept clear or exactly the geometry of the swept over during movement area can be adjusted.
  • the recesses are then dimensioned in such a way that, when the rolling elements 8 are in contact therewith, they are designed in each case on the rolling surfaces on the radially inner rolling surface 9 or the radially outer rolling surface 10 while maintaining a distance for receiving the guide means 19, 20. It must always be ensured that the guide means 16 are free from contact with the additional elements.
  • FIG. 3c illustrates, in a view of a sectional view CC according to FIG. 1, the arrangement of the additional elements in the region of the connection 11.2.
  • the basic structure corresponds to the embodiment in FIG. 3a.
  • the disk-shaped elements 22, 23 have here through openings 35 and 36 for receiving the spacer bolt 12.2. Again, the connection is done by riveting.
  • the rivet connections are designated 17.1, 18.2. Also shown here is the reduced distance a v .
  • FIGS. 4a to 4c illustrate a first variant of a first basic embodiment, in which the means 21 do not comprise additional elements which are designed as elements completely covering the end faces 15A, 15B of the pendulum masses 2A, 2B, but instead locally arranged additional elements in the form of washers 24, 25 and 26, 27.
  • the washers are riveted on both sides between pendulum mass 2A, 2B and standoffs 12.
  • the arrangement of the additional elements in the form of washers 24 to 27 takes place only in the region of the rotationally fixed connections 11.1, 11.2 and in analogy 11.3.
  • the additional elements are arranged only in a portion of the gap, but allow in this a reduction in distance, which prevents tilting due to the arrangement of the compounds 11.1, 11.2, 11.3 between the pendulum masses 2A, 2B over the entire pendulum mass unit 2.
  • Each of the individual joints 11.1, 11.2, 11.3 of the individual pendulum masses 2A and 2B of a pendulum mass unit 2 is characterized by the interposition of such washers 24, 25 in Figure 4a and 26, 27 in Figure 4c.
  • the area of the pendulum bearing arrangements 5.1 in Figure 4b and not shown 5.2 is free of such washers.
  • FIG. 4a illustrates an axial section through the connection 11.1.
  • the washer 24 is disposed between the axial stop surface 13.1 and pendulum mass 2A.
  • the arrangement of the washer 25 takes place between pendulum mass 2B and axial stop surface 14.1. It can be seen that the outer diameter of the washers 24, 25 must be greater than that of the passage opening 37, through which the spacing bolt 12.1 penetrates the pendulum mass carrier 3.
  • the inner diameter of the individual washers 24, 25 is preferably adapted to the diameter of the axial end portions of the spacer pin 12.1.
  • FIG. 4b shows the section B-B according to FIG. 1 for this embodiment. It can be seen that there is no arrangement of washers or spacer filling elements in this area.
  • FIG. 4c illustrates in analogy to FIG. 4a the axial section CC according to FIG. 1 for the connection 11.2.
  • washers 26 and 27 on both sides of the pendulum mass carrier 3 between the axial abutment surfaces 13.2, 14.2 and the pendulum masses 2A, 2B are arranged.
  • the attachment to the pendulum masses 2A, 2B takes place in analogy to the embodiment in Figure 4a.
  • the additional elements in the form of washers 24 to 27 are arranged such that they abut on the axial abutment surfaces 13.1, 13.2 and 14.1, 14.2 in the spacer bolt 12.1, 12.2.
  • the distance bolt 12.1, 12.2 is designed with its region 16.1, 16.2 of smaller width than in a design according to the prior art, as described in Figures 2a to 2c.
  • FIGS. 5a to 5c illustrate a further development of the first variant of the first basic embodiment according to FIGS. 4a to 4c.
  • the axial abutment surfaces 13.1, 13.2 and 14.1, 14.2 designed as abutment surfaces for the individual pendulum masses 2A, 2B, wherein the arrangement of the washers 24, 25 and 26, 27 in the space between pendulum mass carrier 3 and the individual pendulum masses 2A, 2B loose he follows.
  • the washers 23 and 24 do not abut against the pendulum mass carrier 3, which is why the spacer bolts 12.1 and 12.2 in the region of the axial stop surfaces 13.1, 13.2 and 14.1, 14.2 are designed such that this also the washers 24, 25 and for the embodiment in Figure 5c 26, 27 fixed in their position with.
  • the washers are designed in such a way that they are supported in the region of the chamfer or are pressed together with the spacer bolts 12.1, 12.2.
  • FIGS. 6 and 7 Further variants of the first variant of the first basic embodiment are characterized according to FIGS. 6 and 7 by the provision of separate additional elements 28, 29 or 30 integrated or mounted in the individual components of pendulum mass 2A, 2B and / or pendulum mass carrier 3.
  • additional elements 28 to 30 can be variously designed, at least one axial, projecting into the gap projection forming elements such as balls, half shells, cylindrical pins or the like. It is crucial that they produce an axial projection into the gap between pendulum mass 2A, 2B and pendulum mass carrier 3.
  • FIG. 6 shows, on the basis of a sectional view through the connection 11.1 in a view AA according to FIG. 1, an integration of such additional elements 28 and 29 in the form of spherical elements which are mounted or fastened in corresponding receptacles 38, 39 on the individual pendulum masses 2A, 2B.
  • the additional elements 28, 29 are based on the width of the individual pendulum masses 2A, 2B arranged on this or integrated in these, that this at the respective facing end faces 15A, 15B of the individual pen delmassen 2A, 2B each form an axially protruding projection.
  • the arrangement of these additional elements can be done arbitrarily on the pendulum masses 2A, 2B. It is crucial that the localized reduction in distance caused by this, however, takes place outside the range of movement of the guide means 19, 20 in the gap.
  • Figure 7 illustrates an alternative arrangement of such additional elements, here an additional element 30 on pendulum mass carrier 3 in a view B-B of Figure 1.
  • the additional element 30 is designed as a spherical element and mounted in a receptacle 40 on the pendulum mass carrier 3.
  • the additional element 30 is arranged and dimensioned such that it forms an axial projection in the gap.
  • FIGS. 6 and 7 are exemplary. Conceivable are the use of different additional elements as a means 21, which only have to be suitable for the formation of axially projecting areas on the pendulum masses 2A, 2B and / or the pendulum mass carrier 3. These can be movably mounted on the pendulum masses 2A, 2B or the pendulum mass carrier 3 or attached to this or incorporated. When mounting the connection can be force, form or cohesive. The arrangement takes place as a function of the required regions to be generated with a reduction in distance in the gap.
  • Figures 8 to 10 illustrate embodiments of a second variant of a first basic embodiment, i. with integral design of the means 21 on at least one of the components pendulum mass 2A, 2B and / or pendulum mass carrier. 3
  • Figures 8a and 8c illustrate the localized arrangement of stampings 41, 42 on the pendulum masses 2A, 2B in the region of the compound 11.1 and stampings 43, 44 on the pendulum masses 2A, 2B in the region of their realized via the spacer bolt 12.2 compound 11.2.
  • the embossments 41, 42 and 43, 44 are arranged in the region of the passage openings for the standoffs 12.1 and 12.2, respectively, by the pendulum masses 2A, 2B. These are dimensioned in the radial direction in such a way that their outer circumference is arranged on a larger diameter with respect to the spacer bolts 12.1, 12.2. net is as the diameter of the passage opening on the pendulum mass carrier 3.
  • the embossments 41, 42 are designed in the illustrated case such that they rest against the axial stop surfaces 13.1, 14.1 or the embossments 43, 44 on the axial stop surfaces 13.1, 14.2.
  • the areas of reduced distance a v are here generated between the embossments 41 and 43 on the pendulum mass 2A and 42 and 44 on the pendulum mass 2B and the pendulum mass carrier 3.
  • the embossments 41 to 44 preferably describe flat, aligned to the pendulum mass carrier surfaces.
  • the area around the embossings 41, 42 and 43, 44 disposed on the pendulum masses 2A, 2B is free of such embossing and serves to provide the required distance in the range of movement of the guide means 19, 20 of the rolling element 8 between pendulum mass 2A, 2B and pendulum mass carrier.
  • embossments 41, 42 43 and 44 shown in FIGS. 8a to 8c is not mandatory. This can also be done elsewhere on the pendulum mass 2A, 2B, but always to ensure that the range of motion of the guide means 19, 20 of the rolling element 8 remains free.
  • FIG. 8b shows the self-aligning bearing arrangement 5.1, which is free of such embossings.
  • Figures 9a to 9c show a further embodiment in which the means 21 forming embossments are not arranged on the pendulum masses 2A, 2B but the pendulum mass carrier 3.
  • the arrangement of the embossments 45 and 46 takes place here on the pendulum mass carrier 3 outside the range of the track 7 and of the guide means 19, 20 passable area in the gap.
  • the embossments 45, 46 thus form a depression in the receiving region of the rolling element 8 and the raceways, which is characterized by the required minimum distance for receiving the guide means 19, 20.
  • the embossments 45, 46 on the pendulum mass carrier 3 are preferably arranged in the region around the raceways of the individual pendulum bearing arrangements 5.1, 5.2.
  • the remaining areas are preferably free. This can be seen on the sectional views A-A and C-C in Figures 9a and 9c.
  • FIG. 10 Another particularly advantageous embodiment of locally limited surfaces for local reduction of the gap distance is shown in FIG. 10 with reference to a sectional view AA Figure 1 reproduced.
  • the penetrations 47, 48 are formed on the individual pendulum masses 2A, 2B. It is also conceivable embodiment not shown here on pendulum mass carrier. 3
  • the arrangement of the enforcements can be arbitrary. It is also crucial here that the range of movement of the guide means 19, 20 is not affected in the gap and further the projection against a mating surface on the other element, that is arranged in this case the pendulum mass carrier 3. The arrangement is therefore always outside of passage openings on the pendulum mass carrier. 3

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Motorcycle And Bicycle Frame (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

La présente invention concerne un dispositif de pendule centrifuge comprenant au moins un support de masse pendulaire et au moins une masse pendulaire qui est montée sur celui-ci et peut effectuer un mouvement limité radialement et en direction périphérique vis-à-vis du support de masse pendulaire, au moyen d'au moins un élément de roulement à l'intérieur de chemins de roulement formés par des évidements dans le support de masse pendulaire et la masse pendulaire, l'élément de roulement présentant un moyen de guidage formé dans l'espace compris entre masse pendulaire et support de masse pendulaire individuels. L'invention se caractérise en ce qu'à l'extérieur des chemins de roulement destinés à l'élément de roulement et de la zone de l'espace intermédiaire entre la masse pendulaire et le support de masse pendulaire, qui peut être balayée par les moyens de guidage lors du mouvement de roulement de l'élément de roulement, se trouvent des moyens pour réduire de façon au moins localement limitée, l'espace entre la masse pendulaire et le support de masse pendulaire.
PCT/DE2010/001453 2009-12-21 2010-12-13 Dispositif de pendule centrifuge WO2011076169A2 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP10805584.9A EP2516887B1 (fr) 2009-12-21 2010-12-13 Dispositif de pendule centrifuge
CN201080059074.2A CN102762887B (zh) 2009-12-21 2010-12-13 离心力摆装置
JP2012545084A JP5746209B2 (ja) 2009-12-21 2010-12-13 遠心力振り子装置
US13/528,170 US20120255394A1 (en) 2009-12-21 2012-06-20 Centrifugal pendulum mechanism

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102009059755 2009-12-21
DE102009059755.7 2009-12-21
DE102010021410 2010-05-25
DE102010021410.8 2010-05-25

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/528,170 Continuation US20120255394A1 (en) 2009-12-21 2012-06-20 Centrifugal pendulum mechanism

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WO2011076169A2 true WO2011076169A2 (fr) 2011-06-30
WO2011076169A3 WO2011076169A3 (fr) 2011-09-09

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DE102014108146A1 (de) 2013-06-11 2014-12-11 Valeo Embrayages Übertragungseinrichtung mit einer Filtervorrichtung des Typs Pendel-Oszillator sowie Modul für eine Übertragungseinrichtung
JP2014534396A (ja) * 2011-10-19 2014-12-18 ヴァレオ アンブラヤージュ 改良ガイド装置を備えた振り子式振動子タイプのダンパシステム
DE102014108808A1 (de) 2013-06-24 2014-12-24 Valeo Embrayages Drehmomentübertragungsvorrichtung
DE102014011391A1 (de) 2013-08-06 2015-02-12 Valeo Embrayages Schwingungsdämpfungsvorrichtung
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WO2015154768A1 (fr) * 2014-04-09 2015-10-15 Schaeffler Technologies AG & Co. KG Pendule à force centrifuge à montage sur roulement axial
WO2015165669A1 (fr) * 2014-04-28 2015-11-05 Zf Friedrichshafen Ag Atténuateur d'oscillations à amortissement et procédé de production d'un atténuateur d'oscillations à amortissement
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EP3093523A1 (fr) * 2015-05-12 2016-11-16 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3036149A1 (fr) * 2015-05-12 2016-11-18 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
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DE102014211272B4 (de) * 2014-06-12 2022-11-24 Schaeffler Technologies AG & Co. KG Wellenkupplung
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DE112015002910A5 (de) * 2014-06-20 2017-03-02 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
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JP2017129271A (ja) * 2016-01-14 2017-07-27 日本精工株式会社 遠心振り子ダンパ及びトルク伝達装置
EP3404286A4 (fr) 2016-01-14 2020-03-11 NSK Ltd. Amortisseur pendulaire centrifuge et dispositif de transmission de couple
JP6714865B2 (ja) * 2016-11-01 2020-07-01 日本精工株式会社 遠心振り子式ダンパ
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JP6471737B2 (ja) * 2016-10-31 2019-02-20 トヨタ自動車株式会社 捩り振動低減装置
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WO2018199323A1 (fr) * 2017-04-28 2018-11-01 アイシン・エィ・ダブリュ株式会社 Dispositif d'amortissement de vibrations
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WO2012022278A1 (fr) * 2010-08-19 2012-02-23 Schaeffler Technologies Gmbh & Co. Kg Système de pendule à force centrifuge
US9038793B2 (en) 2010-08-19 2015-05-26 Schaeffler Technologies AG & Co. KG Centrifugal pendulum device
JP2014534396A (ja) * 2011-10-19 2014-12-18 ヴァレオ アンブラヤージュ 改良ガイド装置を備えた振り子式振動子タイプのダンパシステム
JP2014534397A (ja) * 2011-10-19 2014-12-18 ヴァレオ アンブラヤージュ 改良ガイド装置を備えた振り子式振動子タイプのダンパシステム
JP2015519526A (ja) * 2012-06-12 2015-07-09 ヴァレオ アンブラヤージュ 安定化された転動要素を備えた振り子式ダンパ装置
KR102182369B1 (ko) * 2012-06-12 2020-11-24 발레오 앙브라이아쥐 안정화된 롤링 요소를 갖는 진자 댐핑 장치
KR20150020300A (ko) * 2012-06-12 2015-02-25 발레오 앙브라이아쥐 안정화된 롤링 요소를 갖는 진자 댐핑 장치
WO2014019582A1 (fr) * 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Poulie pour une masse pendulaire d'un pendule à force centrifuge
US9689463B2 (en) 2012-07-31 2017-06-27 Schaeffler Technologies Gmbh & Co. Kg Roller for a pendulum mass of a centrifugal force pendulum
CN104662327A (zh) * 2012-07-31 2015-05-27 舍弗勒技术股份两合公司 用于离心力摆的摆质量的滚子
DE102014108146A1 (de) 2013-06-11 2014-12-11 Valeo Embrayages Übertragungseinrichtung mit einer Filtervorrichtung des Typs Pendel-Oszillator sowie Modul für eine Übertragungseinrichtung
DE102014108808A1 (de) 2013-06-24 2014-12-24 Valeo Embrayages Drehmomentübertragungsvorrichtung
DE102014011391A1 (de) 2013-08-06 2015-02-12 Valeo Embrayages Schwingungsdämpfungsvorrichtung
FR3009593A1 (fr) * 2013-08-06 2015-02-13 Valeo Embrayages Dispositif d'amortissement vibratoire
CN105452713A (zh) * 2013-08-12 2016-03-30 舍弗勒技术股份两合公司 离心力摆
WO2015021968A1 (fr) * 2013-08-12 2015-02-19 Schaeffler Technologies Gmbh & Co. Kg Pendule à force centrifuge
WO2015154768A1 (fr) * 2014-04-09 2015-10-15 Schaeffler Technologies AG & Co. KG Pendule à force centrifuge à montage sur roulement axial
WO2015165669A1 (fr) * 2014-04-28 2015-11-05 Zf Friedrichshafen Ag Atténuateur d'oscillations à amortissement et procédé de production d'un atténuateur d'oscillations à amortissement
WO2015169306A1 (fr) * 2014-05-06 2015-11-12 Schaeffler Technologies AG & Co. KG Pendule centrifuge présentant un palier à roulement axial
WO2016015725A1 (fr) * 2014-07-28 2016-02-04 Schaeffler Technologies AG & Co. KG Pendule à force centrifuge
EP3093523A1 (fr) * 2015-05-12 2016-11-16 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3036148A1 (fr) * 2015-05-12 2016-11-18 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3036149A1 (fr) * 2015-05-12 2016-11-18 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
EP3101311A1 (fr) * 2015-05-12 2016-12-07 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
WO2017152899A1 (fr) * 2016-03-11 2017-09-14 Schaeffler Technologies AG & Co. KG Pendule centrifuge

Also Published As

Publication number Publication date
EP2516887B1 (fr) 2019-06-19
CN102762887B (zh) 2016-07-20
JP5746209B2 (ja) 2015-07-08
WO2011076169A3 (fr) 2011-09-09
US20120255394A1 (en) 2012-10-11
EP2516887A2 (fr) 2012-10-31
DE102010054254A1 (de) 2011-06-22
CN102762887A (zh) 2012-10-31
JP2013515214A (ja) 2013-05-02

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